WO2022135801A1 - Joint homocinétique grand angle à lubrification optimisée - Google Patents

Joint homocinétique grand angle à lubrification optimisée Download PDF

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Publication number
WO2022135801A1
WO2022135801A1 PCT/EP2021/082122 EP2021082122W WO2022135801A1 WO 2022135801 A1 WO2022135801 A1 WO 2022135801A1 EP 2021082122 W EP2021082122 W EP 2021082122W WO 2022135801 A1 WO2022135801 A1 WO 2022135801A1
Authority
WO
WIPO (PCT)
Prior art keywords
joint
sealing means
central plane
external
kinematic
Prior art date
Application number
PCT/EP2021/082122
Other languages
English (en)
Inventor
Gianni Tenca
Andrea BURATO
Original Assignee
Comer Industries S.P.A.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Comer Industries S.P.A. filed Critical Comer Industries S.P.A.
Publication of WO2022135801A1 publication Critical patent/WO2022135801A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/30—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio
    • F16D3/32—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio by the provision of two intermediate members each having two relatively perpendicular trunnions or bearings
    • F16D3/33—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio by the provision of two intermediate members each having two relatively perpendicular trunnions or bearings with ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/06—Lubrication details not provided for in group F16D13/74

Definitions

  • the present invention relates to a wide-angle constant- velocity joint with optimized lubrication.
  • Wide-angle constant- velocity joints are known which are typically used in cardan shaft transmission systems for agricultural machines, in which the angular offset between the longitudinal axis of the cardan shaft and the longitudinal axis of the driving shaft of the power take-off (PTO) of the tractor and/or of the driven shaft of the work implement to be actuated (PIC) can reach values of several dozen degrees (up to 60°-80°).
  • PTO power take-off
  • PIC driven shaft of the work implement to be actuated
  • These constant- velocity joints of the known type are constituted essentially by a central body which supports two internal forks which protrude along a longitudinal axis on opposite sides of said central body, each fork being coupled to a respective external fork by virtue of the interposition of a corresponding cross.
  • the central body is provided internally with an annular chamber which is extended transversely to the longitudinal axis between the two internal forks and in which a guiding disk or planet gear is accommodated so that it can move by sliding and is connected to tabs which protrude from both external forks.
  • Such tabs are generally associated with spherical heads which are arranged in sliding contact on a cylindrical surface which forms an axial sliding seat provided in the guiding disc along the longitudinal axis.
  • a bushing provided internally with a concave surface shaped like a spherical dome, which is interposed between each spherical head and the cylindrical surface in order to reduce the contact pressures involved and the wear of the components, increasing as a whole the mechanical strength of the joint.
  • the external forks of the joint are designed to be coupled respectively to one of the two ends of the telescopic shaft and to one of the driving shaft of the PTO of the tractor and the transmission shaft of the PIC of the work implement.
  • a pair of guiding rings can be interposed between the internal walls of the chamber and the guiding disk and also can move by sliding transversely to the longitudinal axis.
  • the presence of the rings makes it possible to keep the guiding disk in position during sliding, delimiting laterally the volume of the annular chamber in which the guiding disk moves with respect to the outside environment.
  • the lubrication of the parts in relative motion is generally obtained by leakage of lubricant introduced through the internal chamber of the central body.
  • the lubricant leaks between the guiding disk, the rings, if any, and the internal walls of the chamber, and also between the spherical heads associated with the tabs of the external forks, the spherical sliding bearings, if any, and the axial seat of the guiding disk, and therefore must be replenished periodically.
  • USSN 2002/010027 Al proposes a solution which provides for the use of protective bellows arranged externally to the constant- velocity joint in order to delimit a sealed chamber which contains lubricant, avoiding its dispersion.
  • WO 2008/151223 Al provides for forming, inside the central body, a lubricant reserve ring directly communicating with the internal chamber in order to increase the volume of lubricant that can be accumulated inside it.
  • USSN 2020/132127 Al provides a constant- velocity joint which, in addition to the lubricant reserve ring which communicates with the internal chamber, is provided with sealing rings which are interposed between the walls of said chamber, the guiding rings and the guiding disk and a dosage system which makes it possible to adjust the flow of the lubricant from the reserve ring to the internal chamber.
  • This dosage system consists of a series of calibrated passages for the controlled leakage of the lubricant.
  • the aim of the present invention is to eliminate the drawbacks noted above of the background art, by providing a constant- velocity joint with optimized lubrication which makes it possible to reduce considerably, if not eliminate completely, the consumption and dispersion of lubricant, minimizing the need to perform interventions for maintenance on the components and for replenishment of said lubricant.
  • an object of the present invention is to limit the operating costs of the joint and increase its reliability over time.
  • Another object of the present invention is to not entail structural and constructive complications and to not penalize the overall space occupation of the joint.
  • a further object of the present invention is to provide a structure which is simple, relatively easy to provide in practice, safe in use, effective in operation, and relatively low-cost.
  • Figure 1 is a sectional view, taken along a plane that passes through the longitudinal axis, of a first embodiment of a constant- velocity joint with optimized lubrication according to the invention
  • Figure 2 is a sectional view, taken along a plane that passes through the longitudinal axis, of a variation of the first embodiment of the joint according to the invention
  • Figure 3 is an enlarged-scale view of a portion of Figure 2;
  • Figure 4 is a sectional view of the joint of Figure 2 in the maximum angle position;
  • Figure 5 is an enlarged-scale view of a portion of Figure 4;
  • Figure 6 is a sectional view, taken along a plane that passes through the longitudinal axis, of a further variation of the first embodiment of the joint according to the invention.
  • Figures 6a and 6b are enlarged-scale views of respective details of Figure 6;
  • Figure 7 is a sectional view, taken along a plane that passes through the longitudinal axis, of a second embodiment of the joint according to the invention.
  • Figure 8 is a sectional view, taken along a plane that passes through the longitudinal axis, of a variation of the second embodiment of the joint according to the invention.
  • Figure 9 is an enlarged-scale view of a portion of Figure 8.
  • Figure 10 is a sectional view of the joint of Figure 8 in the maximum angle position
  • Figure 11 is an enlarged-scale view of a portion of Figure 10;
  • Figure 12 is a sectional view, taken along a longitudinal plane, of a universal joint transmission shaft in which the joint according to the invention is applied.
  • the reference numeral 1 generally designates a constant- velocity joint with optimized lubrication.
  • the joint 1 comprises a central body 2 which is associated with two internal forks 3 which protrude on opposite sides along a longitudinal axis A and is provided with an annular chamber 4 which is extended along a central plane (line P in the figures) which is transverse to the longitudinal axis A.
  • the central plane P is substantially perpendicular to the longitudinal axis A.
  • the term "substantially” is understood to mean excluding the conventional machining and assembly tolerances of the components.
  • the central body 2 is composed of two half-shells 2a and 2b which are mutually connected by virtue of threaded elements 6.
  • the central body 2 is provided with a pair of annular flanges 5 which are extended around the longitudinal axis A and are mutually parallel and spaced.
  • Each internal fork 3 is blended with a respective flange 5 on the opposite side of the other of said two flanges.
  • the annular chamber 4 is constituted by an interspace formed between the flanges 5.
  • the mutually facing walls of the flanges 5 form the side walls 4a and the perimetric edge 4b of the chamber 4.
  • the walls 4a can be planar or contoured.
  • Lubricant is introduced in the chamber 4 and is distributed by leaking in order to reduce friction and wear phenomena among the components of the joint 1 in relative motion.
  • the joint 1 furthermore comprises a guiding element 7 which is accommodated so that it can move on the central plane P within the chamber 4.
  • Each internal fork 3 is associated with a respective external fork 8 by interposition of a corresponding cross 9.
  • Conventional bearings are interposed between the pivots of each cross 9 and the prongs of the respective forks 3 and 8.
  • Each external fork 8 is provided with a respective tab 10, which is associated with the guiding element 7 by virtue of relative retention means 11 which form a first kinematic pair 12 adapted to allow at least one degree of freedom in relative translation and a second kinematic pair 13 adapted to allow at least one degree of freedom in relative rotation.
  • the tab 10 has an elongated shape and the inclination of its axis of extension S with respect to the longitudinal axis A can vary as a function of the operating conditions of the joint 1.
  • the joint 1 is sized to allow a transmission of motion up to a relative inclination between the axes of extension S of the tabs 10 equal to a maximum angle (designated by 2a in Figures 4-5, 10-11).
  • the first kinematic pair 12 is of the cylindrical type, in order to allow a relative combined rotary and translational motion of the elements that constitute it.
  • the second kinematic pair 13 is of the spherical type, so as to allow a relative rotation about the three Cartesian axes (three-dimensional rotation) of the elements that constitute it.
  • first sealing means 14 which are interposed between the walls 4a of the chamber 4 and the guiding element 7 and are adapted to prevent the leakage of lubricant between them toward the outside of said chamber.
  • Such first sealing means 14 can provide for one or more conventional first rings, for example made of rubber or other similar material, which are interposed between the walls 4a of the chamber 4 and the guiding element 7.
  • the joint 1 provides for a pair of guiding rings 17 which are interposed between the guiding element 7 and the walls 4a of the chamber 4 on opposite sides of said element along the longitudinal axis A.
  • the first sealing means 14 are interposed between each wall 4a of the chamber 4 and the guiding ring 17 which faces it and between said ring and the guiding element 7.
  • the embodiments shown have a pair of guiding rings 17 shaped like annular plates.
  • the first sealing means 14 comprise a first ring 14a which is interposed between the wall 4a that faces it and the guiding ring 17 and a second ring 14b which is interposed between said guiding ring and the guiding element 7.
  • Each first ring 14a is accommodated in an annular groove which is formed on the wall 4a proximate to the corresponding internal radial end, but it is not excluded that it might be accommodated in the corresponding guiding ring 17.
  • Each second ring 14b is accommodated in an annular groove which is formed on the guiding element 7 proximate to the corresponding external radial end, but it is not excluded that it might be accommodated in the corresponding guiding ring 17.
  • the guiding rings 17 delimit laterally, on opposite sides of the central plane P, the chamber 4 beyond the extension of the side walls 4a formed by the flanges 5.
  • the joint 1 comprises second sealing means 15 which are interposed between the elements of each one of the first kinematic pairs 12 and are adapted to prevent the leaking of lubricant between them toward the outside environment.
  • Such second sealing means 15 can provide for one or more conventional second rings, for example made of rubber or other similar material, interposed between the elements of each one of the first kinematic pairs 12.
  • first and second sealing means 14 and 15 makes it possible to avoid the leaking of the lubricant both outside the chamber 4 and in the region of the first kinematic pairs 12, reducing its dispersion considerably.
  • third sealing means 16 interposed between the elements of each one of the second kinematic pairs 13 and adapted to prevent the leaking of lubricant between them toward the outside environment.
  • the third sealing means 16 can provide for one or more conventional second rings, for example made of rubber or other similar material, interposed between the elements of each one of the second kinematic pairs 13.
  • the guiding element 7 comprises a disk-like element 18 which is arranged at the central plane P and is provided with at least one radial channel 19 the peripheral end of which is open at the chamber 4. Through the radial channel 19, the lubricant leaks from the chamber 4 toward the axial region of the joint 1.
  • radial channels 19 which are angularly spaced around the longitudinal axis A.
  • the peripheral region of the disk-like element 18 is retained between the walls 4a or between the optional guiding rings 17 in all the angular configurations assumed by the joint 1.
  • the guiding element 7 comprises a pair of coupling elements 20 which are substantially parallel to said longitudinal axis A and protrude on opposite sides of the central plane P toward a corresponding external fork 8.
  • the retention means 11 are interposed between the corresponding tab 10 and the corresponding coupling element 20.
  • the retention means 11 comprise a bushing 21, which is provided with an external surface 21a and with an internal surface 21b which is concave and shaped like a spherical dome, and a spherical head 22, coupled to the internal surface 21b, which are interposed between the corresponding tab 10 and the corresponding coupling element 20.
  • the second kinematic pair 13 is formed between the bushing 21 and the spherical head 22.
  • the bushing 21 and the corresponding spherical head 22 constitute what is called a spherical sliding bearing.
  • each coupling element 20 has a longitudinal extension that is at least equal to the value Lmax that corresponds to the maximum distance of the plane of arrangement of the second sealing means 15 from the central plane P in the maximum angle configuration ( Figures 4-5 and 10-11), which is defined by the following equation:
  • L0 is the distance of the plane of arrangement of the second sealing means 15 from the central plane P in the configuration in which the axis of extension S of the tab 10 of the corresponding external fork 8 substantially coincides with the longitudinal axis A ( Figures 3 and 9);
  • central plane C of the cross 9 is understood to reference the plane that is perpendicular to the axis of extension S of the corresponding tab 10 that passes through the intersection point of the axes of the arms of said cross; a is an angle equal to half the angle defined between the axes of extension S of the tabs 10 in the maximum angle configuration.
  • M designates the central diametrical plane of the spherical head 22, i.e., the plane that passes through the center O of said head and is perpendicular to the axis of extension S of the corresponding tab 10 in the first embodiment or to the longitudinal axis A in the second embodiment.
  • each one of the spherical heads 22 has an angular extension on both sides of the corresponding central diametrical plane M that is at least equal to half (angle designated by a in Figures 5 and 11) the angle of maximum inclination (designated by 2a in Figures 5 and 11) that can be obtained between the axes of extension S of the tabs 10 in the maximum angle configuration.
  • the joint 1 can have valve means 23 for limiting the pressure inside the chamber 4 which are associated in fluid communication with said chamber.
  • valve means 23 make it possible to evacuate partially the lubricant accommodated in the chamber 4 if, during filling, an excessive quantity thereof is introduced or if, during the operation of the joint 1, internal overpressures occur which might compromise its functionality.
  • each coupling element 20 is constituted by a sleeve 24, which is extended substantially parallel to the longitudinal axis A and is provided with a substantially cylindrical internal wall 24a, and each tab 10 is constituted by a pivot 25, which is extended along the corresponding axis of extension S.
  • the sleeves 24, in moving on the central plane P remain substantially parallel to the longitudinal axis A as the angular configuration assumed by the joint 1 varies.
  • the spherical head 22 of the retention means For each external fork 8, the spherical head 22 of the retention means
  • the first kinematic pair is integrally associated with a respective pivot 25 and the external surface 21a of the bushing 21 is substantially cylindrical and associated, so as to slide in a direction that is parallel to the longitudinal direction A, with the internal wall 24a of the corresponding sleeve 24.
  • the first kinematic pair is integrally associated with a respective pivot 25 and the external surface 21a of the bushing 21 is substantially cylindrical and associated, so as to slide in a direction that is parallel to the longitudinal direction A, with the internal wall 24a of the corresponding sleeve 24.
  • the internal cavities of the sleeves 24 communicate with each other and with the radial channels 19, so that the lubricant can reach the first and second kinematic pairs 12 and 13.
  • the joint is provided with the first sealing means 14 and with the second sealing means 15.
  • the joint 1 is also provided with the third sealing means 16.
  • the second sealing means 15 comprise a second ring which is partially accommodated in a first annular seat 26 formed on the external surface 21a of the corresponding bushing 21.
  • the second ring 15 protrudes from the corresponding first seat 26 so as to seal the gap formed between the bushing 21 and the sleeve 24, avoiding the leaking of lubricant toward the outside.
  • the first seat 26 might be provided in the internal wall 24a of the sleeve 24.
  • the second sealing means 15 are arranged on the opposite side of the central plane P with respect to the center O of the corresponding spherical head 22. In this manner, the center O is located between the central plane P and the plane of arrangement of the second sealing means 15 for all the angular configurations assumed by the joint 1.
  • the second sealing means 15 are arranged proximately to the end of the bushing 21 that is directed toward the corresponding external fork 8.
  • the third sealing means 16 comprise a third ring which is partially accommodated in a second annular seat 27 formed on the internal surface 21b of the corresponding bushing 21.
  • the third ring 16 protrudes from the corresponding second seat 27 so as to seal the gap formed between the bushing 21 and the spherical head 22, avoiding the leaking of lubricant toward the outside. It is not excluded that the second seat 27 might be provided on the spherical head 22.
  • the third sealing means 16 are arranged on the opposite side of the central plane P with respect to the center O of the corresponding spherical head 22. In this manner, the center O is located between the central plane P and the plane of arrangement of the third sealing means 16 for all the angular configurations assumed by the joint 1.
  • the third sealing means 16 are arranged proximately to the end of the bushing 21 that is directed toward the corresponding external fork 8.
  • the second and third sealing means 15 and 16, respectively, might be arranged at the same distance from the central plane P or at different distances.
  • the valve means 23 comprise a first maximum pressure valve 28 which is accommodated in a through hole 29 formed in one of the flanges 5 and adapted to establish a communication between the chamber 4 and the outside environment.
  • the first valve 28 (shown in detail in Figure 6a) can be of the type of a conventional ball valve.
  • the first valve 28 can be constituted by a valve body 30 provided with an opening 31 for the passage the lubricant which is aligned with the through hole 29 and along which a ball-type flow control element 32 is accommodated so that it can move, being pushed toward an annular abutment seat 33 by a compression spring 34 having an appropriate elastic constant and interposed between said flow control element and an annular shoulder 35 associated with the valve body 30.
  • the valve means 23 can provide for at least one second maximum pressure valve 36 which is accommodated in an axial hole 37 formed in at least one of the pivots 25 along the corresponding axis of extension S and adapted to establish a communication between the region inside the sleeves 24 and the outside environment.
  • the second valve 36 (shown in detail in Figure 6b) can be of the type of a conventional ball valve.
  • the second valve 36 can be shaped in a manner that is fully similar to what has been described above with reference to the first valve 28.
  • each of the coupling elements is constituted by a pivot 38, which is extended in a direction that is substantially parallel to the longitudinal axis A and is provided with a substantially cylindrical external wall 38a, and each one of the tabs 10 comprises a hub 39, which is directed toward the central plane P and is extended along the corresponding axis of extension S.
  • pivots 38 by moving on the central plane P, remain substantially parallel to the longitudinal axis A as the angular configuration assumed by the joint 1 varies.
  • the spherical head 22 of the retention means For each external fork 8, the spherical head 22 of the retention means
  • the external surface 21a of the bushing 21 is substantially cylindrical, but it is not excluded that it might have a different shape which in any case matches the shape of the internal cavity of the hub 39.
  • the joint 1 is provided with the first sealing means 14 and with the second sealing means 15.
  • the joint 1 is also provided with the third sealing means 16.
  • the joint 1 might be provided with the valve means 23 in addition to the sealing means 14, 15, 16.
  • the second sealing means 15 comprise a second ring which is partially accommodated in a first annular seat 41 which is formed in the axial hole 40 of the corresponding spherical head 22.
  • the second ring 15 protrudes from the corresponding first seat 41 so as to seal the gap formed between the axial hole 40 and the pivot 38, avoiding the leakage of lubricant toward the outside. It is not excluded that the first seat 41 might be provided on the pivot 38.
  • the second sealing means 15 are arranged on the same side of the central plane P with respect to the center O of the corresponding spherical head 22. In this manner the plane of arrangement of the second sealing means 15 is located between the center O and the central plane P for all the angular configurations assumed by the joint 1.
  • the second sealing means 15 are arranged proximately to the end of the axial hole 40 that is directed toward the central plane P.
  • the third sealing means 16 comprise a third ring which is partially accommodated in a second annular seat 42 which is formed on the internal surface 21b of the corresponding bushing 21.
  • the third ring 16 protrudes from the corresponding second seat 42 so as to seal the gap formed between the bushing 21 and the spherical head 22, avoiding the leakage of lubricant toward the outside. It is not excluded that the second seat 42 might be provided on the spherical head 22.
  • the third sealing means 16 are arranged on the same side of the central plane P with respect to the center O of the corresponding spherical head 22. In this manner, the plane of arrangement of the third sealing means 16 is located between the center O and the central plane P for all the angular configurations assumed by the joint 1.
  • the third sealing means 16 are arranged proximate to the end of the bushing 21 that is directed toward the central plane P.
  • the second and third sealing means 15 and 16, respectively, can be arranged at the same distance from the central plane P or at different distances.
  • the pivots 38 are provided with respective longitudinal channels 43 which communicate with each other and with the radial channels 19, each of which is open at the respective hub 39 so as to allow the passage of lubricant toward the respective second kinematic path 13.
  • Figure 12 shows a universal joint transmission system 100, which is not described in detail since it is of a known type, which comprises essentially a telescopic shaft 101 constituted by two sections which are associated in mutual longitudinal sliding with respect to each other and is provided, at the opposite ends, with respective universal joint connection assemblies designed to be associated in use respectively with a driving shaft and with a driven shaft.
  • a universal joint transmission system 100 which is not described in detail since it is of a known type, which comprises essentially a telescopic shaft 101 constituted by two sections which are associated in mutual longitudinal sliding with respect to each other and is provided, at the opposite ends, with respective universal joint connection assemblies designed to be associated in use respectively with a driving shaft and with a driven shaft.
  • the driving shaft is the one of the power takeoff of a tractor (PTO) and the driven shaft is the actuation shaft of a work implement (PIC).
  • PTO tractor
  • PIC work implement
  • At least one of the connecting assemblies is constituted by a joint 1 as described above.
  • a joint 1 at one of the ends of the telescopic shaft 101 there is a joint 1 and at the opposite end there is a conventional universal joint 102.
  • a joint 1 according to the invention might be provided at both ends of the telescopic shaft 101.
  • the joint 1 can be used to connect the telescopic shaft 101 both to the driving shaft and to the driven shaft.
  • the described invention achieves the proposed aim and objects, and in particular the fact is stressed that the joint according to the invention makes it possible to reduce, if not eliminate, the consumption and dispersion of lubricant and therefore the need to perform maintenance interventions.
  • first sealing means, the second sealing means and the optional third sealing means act as a barrier against the entry of dust or any other external contamination into the joint according to the invention, preserving its functionality.
  • the joint according to the invention is reliable and durable over time, ensuring optimum lubrication of the components in relative motion.
  • the joint according to the invention does not entail structural complications or increases in space occupation such as to penalize its application.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pivots And Pivotal Connections (AREA)

Abstract

L'invention concerne un joint homocinétique (1) ayant une lubrification optimisée, comprenant un corps central (2) qui est associée à deux fourches internes (3) qui font saillie sur des côtés opposés le long d'un axe longitudinal (A) et comporte une chambre annulaire (4) qui s'étend sur un plan central (P) qui est transversal à l'axe longitudinal (A) et un élément de guidage (7) qui est reçu de façon à pouvoir se déplacer sur ledit plan central (P) dans la chambre annulaire (4). Chacune des fourches internes (3) est associée à une fourche externe respective (8) au moyen de l'interposition d'un croisillon correspondant (9) et chaque fourche externe (8) comporte une languette respective (10) qui est associée à l'élément de guidage (7) grâce à des moyens de retenue relative (11) qui forment une première paire cinématique (12) conçue pour permettre au moins une translation relative et une seconde paire cinématique (13) conçue pour permettre au moins une rotation relative. Le joint (1) comprend en outre des premiers moyens d'étanchéité (14) interposés entre les parois (4a) de la chambre annulaire (4) et l'élément de guidage (7), des seconds moyens d'étanchéité (15) étant associés à chacune des premières paires cinématiques (12).
PCT/EP2021/082122 2020-12-22 2021-11-18 Joint homocinétique grand angle à lubrification optimisée WO2022135801A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT202000031793 2020-12-22
IT102020000031793 2020-12-22

Publications (1)

Publication Number Publication Date
WO2022135801A1 true WO2022135801A1 (fr) 2022-06-30

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7033278B2 (en) 2003-01-03 2006-04-25 Edi Bondioli Wide-angle constant-velocity joint
EP1688632A2 (fr) * 2005-02-04 2006-08-09 Weasler Engineering, Inc. Joint universel avec lubrification amélioré
WO2008151223A1 (fr) 2007-06-05 2008-12-11 Weasler Engineering, Inc. Joint universel avec une meilleure lubrification de rotule
EP3643938A1 (fr) * 2018-10-25 2020-04-29 Edi Bondioli Joint d'accouplement articule a grand angle avec lubrification reservoir

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7033278B2 (en) 2003-01-03 2006-04-25 Edi Bondioli Wide-angle constant-velocity joint
EP1688632A2 (fr) * 2005-02-04 2006-08-09 Weasler Engineering, Inc. Joint universel avec lubrification amélioré
WO2008151223A1 (fr) 2007-06-05 2008-12-11 Weasler Engineering, Inc. Joint universel avec une meilleure lubrification de rotule
EP3643938A1 (fr) * 2018-10-25 2020-04-29 Edi Bondioli Joint d'accouplement articule a grand angle avec lubrification reservoir
US20200132127A1 (en) 2018-10-25 2020-04-30 Edi Bondioli Wide-angle constant velocity joint with lubricant reservoir

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